JP2019050674A - Driving device for vehicle - Google Patents

Abstract

To provide a driving device for a vehicle capable of controlling accurately a motor for outputting a torque for travel of the vehicle, even when a torque is inputted toward the motor from a wheel, or preventing or suppressing deterioration of NVH characteristics caused by resonance.SOLUTION: In a driving device 1 for a vehicle for generating driving force for travel by transmitting a motor torque generated in a motor 2 to a wheel 3, the motor 2 is provided on each wheel 3, and a damper mechanism 5 for mitigating fluctuation of a torque on a power transmission path PT between the motor and the wheel is provided on the power transmission path PT.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a drive device for a vehicle that travels by rotating wheels by a motor.

  Examples of vehicles using a motor as a driving force source are vehicles using a conventional internal combustion engine (engine), a vehicle having a transmission replaced with a motor, an in-wheel motor having a motor incorporated in a wheel, etc. Describes an example of a drive device in a vehicle equipped with an in-wheel motor. In the device, a Ravigneaux planetary gear mechanism is disposed coaxially with the motor shaft, a sun gear is integrated with the motor shaft, a ring gear is fixed to the motor case, and a carrier is connected to the wheel hub shaft. There is. The planetary gear mechanism is configured to function as a reduction mechanism, so that the torque output by the motor is amplified by the planetary gear mechanism and transmitted to the wheel, and the vehicle travels with the torque output by the motor.

JP, 2016-201945, A

  In the configuration described in Patent Document 1, the motor shaft for outputting torque and the tire wheel are substantially directly connected, and the motor outputs the torque corresponding to the current and the number of revolutions according to the frequency. As it rotates, the control response of the driving force is good, and the driving force can be stabilized and smooth traveling can be performed. However, the motor is subjected to resistance (travel resistance) as the vehicle travels, and the travel resistance changes successively and frequently due to the unevenness of the road surface. Also, each time the driver performs acceleration / deceleration operation, the load on the motor changes. When the running resistance changes or the load applied to the motor due to the braking operation increases, the motor is controlled to satisfy the drive request at that time. As described in Patent Document 1, when the tire wheel and the motor are in a so-called direct connection state, a load applied to the tire or a change in torque input from the tire toward the motor acts directly on the motor, Control of the motor corresponding to such a change. Therefore, for example, by traveling on the uneven road surface, the torque input from the tire to the motor repeatedly changes, and when it is in a fluctuating state, the control of the motor is accurate against such vibration. As a result, the driving force may be momentarily or temporarily insufficient, or may be excessively large. Further, in the synchronous motor, there is a possibility that the synchronization may be disturbed by the vibration of the torque input from the tire. As described above, in the drive device for a vehicle in which the wheels are driven by the motor, the controllability deteriorates due to the influence of the torque input from the tire due to the road surface or the operation of the driver, or the energy efficiency decreases. There is a possibility that the frequent and large change of the output torque may deteriorate the NVH characteristics of the vehicle.

  The present invention has been made focusing on the above technical problems, and even when torque is input from the wheel to the motor, the control of the motor for outputting the torque for traveling the vehicle is accurate. It is an object of the present invention to provide a vehicle drive device capable of performing well or preventing or suppressing deterioration of the NVH characteristics due to resonance.

  In order to achieve the above object, the present invention relates to a vehicle drive apparatus for transmitting a motor torque generated by a motor to wheels to generate a driving force for traveling, wherein the motor is provided for each wheel A damper mechanism is provided in the power transmission path to reduce torque fluctuation in the power transmission path between the motor and the wheel.

  Further, in the present invention, a reduction mechanism is provided on the power transmission path so that the number of revolutions of the wheel is lower than the number of revolutions of the motor, and the damper mechanism includes the motor. A first member disposed on the output side of the motor in the direction of transmission of the motor torque generated by the first motor, and a first member disposed on the output side of the first member in the direction of transmission of the motor torque generated by the motor A spring type damper having two members and an elastic body connecting the first member and the second member so as to be capable of relative rotation, the spring type damper transmitting direction of the motor torque generated by the motor May be provided on the output side of the speed reduction mechanism.

  Furthermore, in the present invention, a reduction gear mechanism is provided on the power transmission path so that the number of rotations of the wheel is low relative to the number of rotations of the motor, and the damper mechanism The invention may include a pendulum damper having an inertial mass that reduces variations in the torque by reciprocating due to variations in the torque in the transmission path.

  Furthermore, in the present invention, the damper mechanism includes a first member disposed on the output side of the motor in the transmission direction of the motor torque generated by the motor, and a transmission direction of the motor torque generated by the motor. The spring-type damper may further include a second member disposed on the output side of the first member, and an elastic body connecting the first member and the second member so as to allow relative rotation.

  In the present invention, the damper mechanism further includes a planetary rotation mechanism that performs a differential operation by a plurality of rotation elements, and the first member is connected to a first rotation element of the plurality of rotation elements, The second member is connected to a second rotation element of the plurality of rotation elements, and the first rotation element and the second rotation element are relatively rotated by the fluctuation of the torque in the power transmission path. The third of the plurality of rotating elements may be configured to rotate to produce an inertial torque.

  According to the present invention, when the load applied to the wheel is changed due to the unevenness of the road surface and the torque fluctuation occurs on the power transmission path between the wheel and the motor accordingly, the torque fluctuation is Absorbed or reduced by twisting. Therefore, the controllability and efficiency of the motor and the deterioration of the NVH characteristics of the vehicle can be avoided or suppressed. As a result, so-called robustness can be improved as a whole of the vehicle drive device. Further, since the control of the motor can be performed with high accuracy, so-called power consumption can be improved.

FIG. 1 is a view schematically showing a part of a so-called in-wheel motor vehicle configured using a vehicle drive device according to an embodiment of the present invention. It is a skeleton figure showing the drive for vehicles concerning a 1st embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 2nd embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 3rd embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 4th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 5th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 6th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 7th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning an 8th embodiment of this invention. It is a figure which shows typically the pendulum type | mold damper shown in FIG. It is a skeleton figure showing the drive for vehicles concerning a 9th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning a 10th embodiment of this invention. It is a skeleton figure showing the drive for vehicles concerning an 11th embodiment of this invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows typically a part of what is called on-board type vehicle which mounted the vehicle drive device which concerns on embodiment of this invention in the vehicle body.

First Embodiment
A vehicle drive device according to an embodiment of the present invention is a device that generates a driving force for traveling of a vehicle, and the vehicle drive device is provided for each wheel in the vehicle. FIG. 1 is a view schematically showing a part of a so-called in-wheel motor vehicle that is configured using a vehicle drive device according to an embodiment of the present invention. The vehicle drive device 1 shown in FIG. 1 includes a motor 2 as a driving force source, and is configured to transmit the motor torque generated by the motor 2 to the wheels 3. That is, the driving force generated by each wheel 3 can be controlled independently. The torque transmission path PT for transmitting the motor torque generated by the motor 2 to the wheels 3 corresponds to the power transmission path in the embodiment of the present invention. Moreover, the motor torque mentioned above is only described as torque in the following description.

  A reduction mechanism 4 is provided on the output side of the motor 2 in the direction of transmission of the torque generated by the motor 2 so that the number of rotations of the wheel 3 is lower than the number of rotations of the motor 2. Therefore, the torque generated by the motor 2 is increased and transmitted to the wheel 3, and a low torque high rotation type motor, that is, one with a small outer diameter can be adopted as the motor 2. On the output side of the reduction mechanism 4 in the transmission direction of the torque generated by the motor 2, that is, between the reduction mechanism 4 and the wheel 3, the unevenness of the road surface on which the vehicle travels or the driver's operation A damper mechanism 5 is provided to reduce or mitigate so-called reverse input torque that is input toward the direction. The wheels 3 are connected to the output side of the damper mechanism 5 in the direction of transmission of the torque generated by the motor 2. Specifically, the output shaft of the damper mechanism 5 is connected to the wheel 7 on which the tire 6 of the wheel 3 is mounted.

  The motor 2, the speed reduction mechanism 4, and the damper mechanism 5 described above are accommodated in the case 8, and the case 8 is attached to the wheel 7 so as to be relatively rotatable. The case 8 is supported by the vehicle body 11 by a suspension mechanism 9 and a lower arm 10.

  FIG. 2 is a skeleton diagram showing the vehicle drive device according to the first embodiment of the present invention. As shown in FIG. 2, the stator 2S of the motor 2 is fixed to the case 8, and the rotor 2R is connected to the reduction gear mechanism 4 so as to be able to transmit torque. The motor 2 may be configured to perform energy regeneration at the time of deceleration, and as a motor performing energy regeneration at the time of deceleration, for example, a motor having a power generation function such as a permanent magnet synchronous motor can be mentioned. In FIG. 2, the suspension mechanism 9 and the lower arm 10 are omitted to simplify the drawing.

  In the example shown in FIG. 2, the reduction gear mechanism 4 is configured by a planetary gear mechanism corresponding to the planetary rotation mechanism in the embodiment of the present invention, and is arranged on the same axis as the motor 2. The reduction gear mechanism 4 includes a sun gear 4S, a large diameter first pinion gear 4P1 engaged with the sun gear 4S, a second pinion gear 4P2 which rotates integrally with the first pinion gear 4P1 and smaller in diameter than the first pinion gear 4P1 and a second pinion gear 4P2. A ring gear 4R which is an internal gear disposed concentrically with respect to the sun gear 4S while meshing, and a carrier 4C which holds the first pinion gear 4P1 and the second pinion gear 4P2 so as to be capable of rotating and revolving. The rotor 2R of the motor 2 is connected to the sun gear 4S, and the torsional damper 12 corresponding to the spring-type damper in the embodiment of the present invention is connected to the carrier 4C. That is, in the example shown in FIG. 2, the damper mechanism 5 described above is configured by the torsional damper 12. The ring gear 4R is fixed to the case 8. Therefore, the torque input to the sun gear 4S is increased according to the gear ratio of the reduction mechanism 4 and output from the carrier 4C. In addition, by adopting the planetary gear mechanism as the reduction mechanism 4 in this manner, the overall size of the vehicle drive device 1 can be reduced.

  The torsional damper 12 is disposed on the output side of the reduction mechanism 4 in the transmission direction of the torque generated by the motor 2. The torsional damper 12 includes an input side rotation member 12A, an output side rotation member 12B disposed on the downstream side of the input side rotation member 12A in the transmission direction of the torque generated by the motor 2, and the input side rotation member 12A and their outputs. It is comprised by 12 A of coil springs which connect the side rotation member 12B so that relative rotation is possible. The carrier 4C of the reduction gear mechanism 4 is connected to the input side rotation member 12A, and the wheel 3 is connected to the output side rotation member 12B. The input side rotation member 12A corresponds to a first member in the embodiment of the present invention, the output side rotation member 12B corresponds to a second member in the embodiment of the present invention, and the coil spring 12C is an elastic member in the embodiment of the present invention. It corresponds to the body.

  Next, the operation of the vehicle drive device 1 configured as shown in FIG. 2 will be described. When the motor 2 is subjected to powering control and outputs torque, the output torque of the motor 2 is increased according to the gear ratio in the reduction mechanism 4 and transmitted to the input-side rotating member 12A of the torsional damper 12 via the coil spring 12C. The torque is transmitted to the output side rotation member 12B of the torsional damper 12. Since the wheel 3 is connected to the output side rotation member 12B, torque for rotating the output side rotation member 12B and the wheel 3 acts on the coil spring 12C as a reaction force. The torque acting as a reaction force on the coil spring 12C is simply referred to as a reaction torque in the following description. A load for compressing the coil spring 12C is generated by the output torque of the motor 2 and the reaction torque transmitted to the input side rotation member 12A, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. That is, it twists. In the case where the output torque of the motor 2 or the reaction torque, that is, the torque transmitted through the power transmission path between the motor 2 and the wheel 3 does not fluctuate or is stable, the above-mentioned torsion occurs. The entire torsional damper 12 rotates integrally.

  The case where torque in the reverse rotation direction, so-called reverse input torque, acts on the wheel 3 due to the unevenness of the road surface on which the vehicle travels and the operation of the driver will be described. For example, when the wheel 3 rides on or collides with a step on the road surface, the reverse input torque Ti acts on the wheel 3 instantaneously or in an impulsive manner. Since the reverse input torque Ti acts to reversely rotate the wheel 3, the angular velocity and the angular acceleration of the output side rotation member 12B are reduced by the reverse input torque Ti, and the above-mentioned reaction torque is increased. As a result, the load for compressing the coil spring 12C is increased, and the coil spring 12C is further compressed. On the other hand, when the reverse input torque Ti becomes smaller or comes off, the reaction torque decreases. As a result, the load that compresses the coil spring 12C decreases and the coil spring 12C expands or restores, and the elastic force of the coil spring 12C acts to increase the angular velocity or angular acceleration of the output side rotation member 12B. Such expansion and contraction of the coil spring 12C occur repeatedly according to the vibration of the reverse input torque Ti.

  Therefore, in the configuration described above, the expansion and contraction of the coil spring 12C in the torsional damper 12 causes the torque T1 in which the reverse input torque Ti is reduced to appear in the input side rotation member 12A. That is, it is possible to reduce or alleviate the fluctuation of the torque caused by the reverse input torque Ti or the reverse input torque Ti input from the wheel 3 to the motor 2. Therefore, control of the motor can be performed with high accuracy, and efficiency can be improved, and so-called electricity cost can be improved. In addition, since fluctuations in torque in the power transmission path can be reduced or mitigated, for example, the meshing state of the gears in the reduction gear mechanism 4 is changed to prevent or suppress generation of rattling noise and vibrations resulting therefrom. be able to. Furthermore, since the motor 2 is not performing powering control, that is, in a so-called free state, resonance between the vibration of the motor 2 and the vibration of the reverse input torque Ti in the case where the natural frequency is decreasing is suppressed. Can. That is, the deterioration of the NVH characteristics can be avoided or suppressed. As a result, so-called robustness can be improved as a whole of the vehicle drive device 1.

Second Embodiment
FIG. 3 is a skeleton diagram showing a vehicle drive system according to a second embodiment of the present invention. The example shown in FIG. 3 is an example in which the damper mechanism in the embodiment of the present invention is configured by the torsional damper 12 and the planetary gear mechanism 13. The planetary gear mechanism 13 is of a single pinion type, and holds a sun gear 13S, a ring gear 13R which is an internal gear disposed concentrically with the sun gear 13S, and a pinion gear 13P engaged with the sun gear 13S and the ring gear 13R. And a carrier 13C. The input side rotation member 12A of the torsional damper 12 is connected to the carrier 13C, and the output side rotation member 12B of the torsion damper 12 is connected to the sun gear 13S. An inertial mass body 14 having a predetermined mass is integrally provided on the ring gear 13R. Since the other configuration is the same as that shown in FIG. 2, the same parts as those shown in FIG. 2 are assigned the same reference numerals as in FIG. 2 and the description thereof is omitted.

  The operation of the vehicle drive system 1 configured as shown in FIG. 3 will be described. When the motor 2 outputs a torque, the output torque is increased according to the gear ratio in the reduction mechanism 4 and is transmitted to the input side rotation member 12A of the torsional damper 12. A load for compressing the coil spring 12C is generated by the output torque of the motor 2 transmitted to the input side rotation member 12A and the above-described reaction torque, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. Since the sun gear 13S of the planetary gear mechanism 13 is connected to the output side rotation member 12B and the carrier 13C is connected to the input side rotation member 12A, the relative rotation between the input side rotation member 12A and the output side rotation member 12B The sun gear 13S and the carrier 13C rotate relative to each other by a predetermined angle. When there is no fluctuation in torque transmitted through the power transmission path between the motor 2 and the wheel 3 or when the torque is stable, the entire torsional damper 12 is integrated in a state in which the above-described torsion occurs. To rotate. Similarly, since the sun gear 13S and the carrier 13C integrally rotate in a twisted state, the entire planetary gear mechanism 13 integrally rotates.

  When the reverse input torque Ti is input to the wheel 3 due to the unevenness of the road surface or the operation of the driver, the compressive force acting on the coil spring 12C changes. For example, a load that further compresses the coil spring 12C is generated, and the load further compresses the coil spring 12C. Then, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other. Thus, the reverse input torque Ti is reduced and transmitted to the input side rotation member 12A. Thus, in the following description, the torque appearing on the input side rotation member 12A is referred to as a damper passing torque T1 for the sake of convenience. Furthermore, relative rotation between the sun gear 13S and the carrier 13C occurs with relative rotation between the input side rotation member 12A and the output side rotation member 12B.

  Since the relative rotation between the input side rotation member 12A and the output side rotation member 12B is repeatedly generated by the vibration of the reverse input torque Ti, the relative rotation between the sun gear 13S and the carrier 13C is repeatedly generated according to the vibration of the reverse input torque Ti. Along with this, the pinion gear 13P of the planetary gear mechanism 13 rotates within a predetermined angle range, and the ring gear 13R is forcibly rotated. The ring gear 13R vibrates according to the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the ring gear 13R, the mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Further, in the example shown here, the rotational speed of the ring gear 13R is accelerated with respect to the rotational speed of the carrier 13C according to the gear ratio. Therefore, the rotational angular acceleration of the ring gear 13R and the inertial mass body 14 is increased, and the inertial torque T2 is increased accordingly. The inertia torque T2 acts on the input side rotation member 12A. Further, the phase of the vibration of the above-mentioned inertia torque T2 and the phase of the vibration of the damper passing torque T1 transmitted to the input side rotation member 12A through the torsional damper 12 are deviated. Therefore, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is reduced by the inertia torque T2 and becomes smooth. As described above, in the second embodiment, since the damper passing torque T1 appearing in the input side rotation member 12A can be reduced by the inertia torque T2, the reverse input torque Ti transmitted to the motor 2 and the torque fluctuation due to it can be reduced. It can be reduced or mitigated more effectively than the first embodiment. As a result, the control of the motor 2 can be performed with high accuracy, and the efficiency can be improved, and so-called electricity costs can be improved. Furthermore, it is possible to avoid or suppress the occurrence of gear rattling noise and vibration due to changes in the meshing state of the gears meshing with each other in the reduction gear mechanism 4 and the planetary gear mechanism 13. As described above, even in the second embodiment, the same operation and effect as those of the first embodiment can be obtained.

Third Embodiment
FIG. 4 is a skeleton diagram showing a vehicle drive system according to a third embodiment of the present invention. The damper mechanism in the third embodiment is a device in which the configuration of a part of the planetary gear mechanism in the damper mechanism shown in FIG. 3 is changed, and in the third embodiment, the output side rotating member 12B of the torsional damper 12 on the carrier 13C. Are connected, the input-side rotation member 12A is connected to the ring gear 13R, and the inertia mass body 14 is provided on the sun gear 13S. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 are assigned the same reference numerals as in FIG. 3 and the description thereof is omitted.

  The operation of the third embodiment will be described. As described above, in the case where the motor 2 outputs a torque and there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3 The whole of the torsional damper 12 rotates integrally. In addition, the entire planetary gear mechanism 13 rotates integrally.

  When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the carrier 13C in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P in the planetary gear mechanism 13 rotates within a predetermined angle range, and the sun gear 13S is forcibly rotated. The sun gear 13S vibrates according to the vibration of the reverse input torque Ti. Since the inertia mass body 14 is integrally provided on the sun gear 13S, the mass (inertial moment) obtained by adding the mass of the sun gear 13S and the mass of the inertia mass body 14 and the inertia torque T2 according to the rotational angular acceleration are It occurs. Further, in the example shown here, the rotational speed of the sun gear 13S is accelerated with respect to the rotational speed of the ring gear 13R according to the gear ratio. Therefore, the rotational angular acceleration of the sun gear 13S and the inertial mass body 14 is increased, and the inertial torque T2 is increased accordingly. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Therefore, the reverse input torque Ti transmitted to the motor 2 and the variation of the torque resulting therefrom are reduced or mitigated, so that even in the third embodiment, the same operation and effect as the second embodiment can be obtained. it can.

Fourth Embodiment
FIG. 5 is a skeleton diagram showing a vehicle drive system according to a fourth embodiment of the present invention. The damper mechanism in the fourth embodiment is a device in which the configuration of a part of the planetary gear mechanism in the damper mechanism shown in FIG. 3 is changed, and in the fourth embodiment, the inertia mass body 14 is provided on the carrier 13C, and the ring gear 13R. The input side rotation member 12A of the torsional damper 12 is connected to the sun gear 13S, and the output side rotation member 12B is connected to the sun gear 13S. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

  The operation of the fourth embodiment will be described. As described above, in the case where the motor 2 outputs a torque and there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3 The whole of the torsional damper 12 rotates integrally. In addition, the entire planetary gear mechanism 13 rotates integrally.

  When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the sun gear 13S and the ring gear 13R in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the carrier 13C is forcibly rotated, and vibrates in accordance with the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the carrier 13C, the mass (inertial moment) obtained by adding the mass of the carrier 13C and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the fourth embodiment, it is possible to obtain the same operation and effect as the respective embodiments described above. Can.

Fifth Embodiment
FIG. 6 is a skeleton diagram showing a vehicle drive system according to a fifth embodiment of the present invention. The damper mechanism in the fifth embodiment is a device in which the configuration of a part of the planetary gear mechanism in the damper mechanism shown in FIG. 3 is changed. In the fifth embodiment, the output-side rotation member 12B of the torsional damper 12 is connected to the carrier 13C, the input-side rotation member 12A is connected to the sun gear 13S, and the inertial mass body 14 is provided on the ring gear 13R. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

  The operation of the fifth embodiment will be described. As described above, in the case where the motor 2 outputs a torque and there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3 The whole of the torsional damper 12 rotates integrally. In addition, the entire planetary gear mechanism 13 rotates integrally.

  When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the carrier 13C and the sun gear 13S in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the ring gear 13R is forcibly rotated, and the ring gear 13R vibrates according to the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the ring gear 13R, the mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is reduced and smoothed. become. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the fifth embodiment, the same operation and effect as each embodiment can be obtained. .

Sixth Embodiment
FIG. 7 is a skeleton diagram showing a vehicle drive system according to a sixth embodiment of the present invention. The damper mechanism in the sixth embodiment is a device in which the configuration of a part of the planetary gear mechanism in the damper mechanism shown in FIG. 3 is changed, and in the sixth embodiment, the inertia mass body 14 is provided on the carrier 13C, and the sun gear 13S The input side rotation member 12A of the torsional damper 12 is connected to the ring gear 13R, and the output side rotation member 12B is connected to the ring gear 13R. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 are assigned the same reference numerals as in FIG. 3 and the description thereof is omitted.

  The operation of the sixth embodiment will be described. As described above, in the case where the motor 2 outputs a torque and there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3 The whole of the torsional damper 12 rotates integrally. In addition, the entire planetary gear mechanism 13 rotates integrally.

  When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the sun gear 13S in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the carrier 13C is forcibly rotated, and vibrates in accordance with the vibration of the reverse input torque Ti. Then, a mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and an inertial torque T2 according to the rotational angular acceleration are generated. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or alleviated, so that even in the sixth embodiment, the same operation and effect as each of the above-described embodiments can be obtained. Can.

Seventh Embodiment
FIG. 8 is a skeleton diagram showing a vehicle drive system according to a seventh embodiment of the present invention. The damper mechanism in the seventh embodiment is a device in which the configuration of a part of the planetary gear mechanism in the damper mechanism shown in FIG. 3 is changed, and in the seventh embodiment, the input side rotation member 12A of the torsional damper 12 on the carrier 13C. Are connected, the output side rotation member 12B is connected to the ring gear 13R, and the inertial mass body 14 is provided on the sun gear 13S. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

  The operation of the seventh embodiment will be described. As described above, in the case where the motor 2 outputs a torque and there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3 The whole of the torsional damper 12 rotates integrally. In addition, the entire planetary gear mechanism 13 rotates integrally.

  When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the carrier 13C in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P is rotated within a predetermined angle range, the sun gear 13S is forcibly rotated, and vibrates according to the vibration of the reverse input torque Ti. Then, a mass (inertial moment) obtained by adding the mass of the sun gear 13S and the mass of the inertial mass body 14 and an inertial torque T2 according to the rotational angular acceleration are generated. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the seventh embodiment, the same operation and effect as each of the above-described embodiments can be obtained. Can.

Eighth Embodiment
An eighth embodiment of the present invention is shown in FIG. The example shown in FIG. 9 is an example which comprised the damper mechanism in embodiment of this invention by the pendulum type damper mechanism. The pendulum type damper mechanism is referred to as a pendulum type damper 15 in the following description. The pendulum type damper 15 is provided on the output side of the motor 2 in the transmission direction of the torque generated by the motor 2 and on the input side of the reduction mechanism 4 in the example shown here.

  FIG. 10 is a view schematically showing the pendulum type damper shown in FIG. As shown in FIG. 10, the pendulum type damper 15 includes a rotating body 16 that rotates integrally with the rotor 2R, and a plurality of rolling chambers are provided on the outer peripheral portion of the rotating body 16 at regular intervals in the circumferential direction 17 are formed. The rolling chamber 17 is a penetrating portion formed by penetrating the rotating body 16 in the plate thickness direction, that is, in a direction parallel to the central axis of rotation of the rotating body 16, and in the example shown in FIG. It is formed in four places in. As shown in FIG. 10, the shape is a shape which is more curved than the outer peripheral surface of the rotary body 16, and in a simulated manner, it is a shape which is an oval or an oval. In each of the rolling chambers 17 is accommodated a rolling element 18 that performs a pendulum motion with an inertial force when the torque of the rotating body 16 changes. The rolling element 18 is pressed against the inner wall surface of the inner wall surface of the rolling chamber 17 in the radial direction of the rotating member 16 by centrifugal force when the rotating member 16 rotates, and rolls along the inner wall surface. Is configured as. Therefore, the inner surface is the rolling surface 19. The portion of the rolling element 18 in contact with the rolling surface 19 is configured to have a circular cross section. Therefore, the rolling element 18 may be a simple cylindrical or cylindrical member, or may have flanges at both ends.

  A cover 20 is attached to the outer peripheral side of the rotating body 16. The cover 20 is for shielding the rolling chamber 17 and the rolling element 18 from dust to compensate for the smooth pendulum movement of the rolling element 18. As shown in FIGS. 9 and 10, the cover 20 has a hollow ring shape as a whole, and the hollow portion has a box-shaped cross section (rectangular cross section) covering the rolling chamber 17 and the rolling element 18. Since the other configuration is the same as the configuration shown in FIG. 2 described above, the same portions as the configuration shown in FIG. 2 will be assigned the same reference numerals as in FIG. 2 and the description thereof will be omitted.

  The operation of the eighth embodiment will be described. When the motor 2 outputs a torque and the rotating body 16 rotates, the rolling elements 18 also rotate accordingly. The rolling element 18 is moved to a position farthest from the center of the rotating body 16 in the rolling chamber 17 by the centrifugal force. That is, the rolling element 18 moves to a position on the rolling surface 19 farthest from the center of the rotating body 16. When there is no or stable fluctuation of the torque transmitted through the power transmission path between the motor 2 and the wheel 3, the rolling element 18 is located at the most from the center of rotation of the rotating body 16 on the rolling surface 19. It is pushed by centrifugal force to a distant place.

  When the reverse input torque Ti is input to the wheel 3 and the torque in the power transmission path between the motor 2 and the wheel 3, that is, the torque of the rotating body 16 changes, the rotational speed of the rotating body 16 changes. Along with this, the rolling element 18 performs a pendulum motion inside the rolling chamber 17 by inertia force. That is, it reciprocates along the rolling surface 19 in a state where it is pressed against the rolling surface 19 by the centrifugal force. Such a deviation between the torsional vibration of the rotating body 16 and the pendulum motion of the rolling element 18 reduces torque fluctuation in the reverse input torque Ti and the power transmission path resulting therefrom. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the eighth embodiment, the same operation and effect as each embodiment described above can be obtained. Can.

  By the way, when the vehicle travels at a high vehicle speed, the reverse input torque may be periodically input due to unevenness of the road surface on which the vehicle travels. In the pendulum type damper 15 of the above configuration, the rolling element 18 reciprocates due to the fluctuation of the transmitted torque. Therefore, a so-called pendulum, which is the length from the rocking fulcrum of rolling element 18 that performs pendulum movement to the center of gravity of rolling element 18, to reciprocate according to the vibration of the reverse input torque input when traveling at high vehicle speeds. Change the length. The pendulum length according to the vibration of the reverse input torque input when traveling at a high vehicle speed can be obtained in advance, for example, by experiment. By changing the pendulum length to reciprocate according to the vibration of the reverse input torque that is input when traveling at high vehicle speeds, when traveling at high vehicle speeds and the reverse input torque is periodically input Even if it is, the vibration due to the periodic reverse input torque can be reduced. As a result, in addition to preventing or suppressing the transmission of the above-described vibration to the motor 2, it is possible to prevent or suppress the transmission of the above-described vibration to the vehicle compartment. So-called road noise can be reduced to improve quietness.

The ninth embodiment
FIG. 11 is a skeleton diagram showing a vehicle drive system according to a ninth embodiment of the present invention. The example shown in FIG. 11 is an example in which the pendulum type damper 15 is disposed between the motor 2 and the reduction mechanism 4 in the transmission direction of the torque generated by the motor 2 and the torsional damper 12 is disposed on the output side of the reduction mechanism 4 It is. Since the other configuration is the same as that shown in FIG. 9, the same parts as those shown in FIG. 9 will be assigned the same reference numerals as in FIG. 9 and will not be described.

  The operation of the ninth embodiment will be described. When the motor 2 outputs a torque and the rotating body 16 rotates, the rolling elements 18 also rotate accordingly. The rolling element 18 moves to the farthest point from the center of the rotating body 16 on the rolling surface 19 by centrifugal force. Further, a load that the coil spring 12C compresses is generated by the output torque of the motor 2 transmitted to the input side rotation member 12A and the above-described reaction torque, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. If there is no torque fluctuation in the power transmission path between the motor 2 and the wheel 3 or if it is stable, the rolling elements 18 are centrifugal force at a position farthest from the center of the rotating body 16 on the rolling surface 19 Keep pressed by. Further, in the torsional damper 12, the entire torsional damper 12 rotates integrally as a result of the above-described torsion.

  When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. By such expansion and contraction of the coil spring 12C, the reverse input torque Ti is reduced and transmitted to the input side rotation member 12A. The damper passing torque T1 appearing on the input side rotation member 12A is transmitted to the pendulum type damper 15 via the speed reduction mechanism 4. When the rotational speed of the rotating body 16 is changed by the damper passing torque T1, the rolling element 18 performs a pendulum motion inside the rolling chamber 17 by an inertial force. That is, it reciprocates along the rolling surface 19 in a state where it is pressed against the rolling surface 19 by the centrifugal force. Such a deviation between the torsional vibration of the rotating body 16 and the pendulum motion of the rolling element 18 reduces the damper passing torque T1. That is, in the ninth embodiment, the reverse input torque Ti is reduced to two stages by the torsional damper 12 and the pendulum damper 15. Therefore, even in the ninth embodiment, since the fluctuation of the reverse input torque Ti transmitted to the motor 2 and the torque resulting therefrom is reduced or mitigated, the same operation and effect as each embodiment can be obtained. . Further, as in the eighth embodiment, the pendulum length in the pendulum type damper 15 is adjusted so that the rolling elements 18 reciprocate according to the periodic reverse input torque input when traveling at a high vehicle speed. Thus, it is possible to reduce the vibration due to the periodic reverse input torque Ti when traveling at a high vehicle speed.

Tenth Embodiment
FIG. 12 is a skeleton diagram showing a vehicle drive system according to a tenth embodiment of the present invention. The example shown in FIG. 12 is an example in which the arrangement of the pendulum type damper 15 shown in FIG. 11 is changed. That is, the pendulum type damper 15 is disposed on the output side of the reduction mechanism 4 in the direction of transmission of the torque generated by the motor 2, and the torsional damper 12 is disposed on the output side of the pendulum type damper 15. Since the other configuration is the same as that shown in FIG. 11, the same parts as those shown in FIG. 11 will be assigned the same reference numerals as in FIG. 11 and the description thereof will be omitted.

  The operation of the tenth embodiment will be described. When the motor 2 outputs a torque, the torque is increased according to the gear ratio of the reduction mechanism 4 and is transmitted to the pendulum type damper 15. When the rotating body 16 is rotated by the transmitted torque, the rolling element 18 is also rotated accordingly. The rolling element 18 moves to the farthest point from the center of the rotating body 16 on the rolling surface 19 by centrifugal force. Further, the coil spring 12C is compressed by the output torque of the motor 2 transmitted to the input side rotation member 12A and the reaction torque described above, and the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. . When there is no torque fluctuation transmitted through the power transmission path between the motor 2 and the wheel 3 or when it is stable, the rolling element 18 is located at the farthest point from the center of the rotating body 16 on the rolling surface 19 Keep pressed by centrifugal force. Further, in the torsional damper 12, the entire torsional damper 12 rotates integrally as a result of the above-described torsion.

  When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. By such expansion and contraction of the coil spring 12C, the reverse input torque Ti is reduced and transmitted to the input side rotation member 12A. A damper passing torque T1 appears on the input side rotation member 12A, and the damper passing torque T1 is transmitted to the pendulum damper 15. In the pendulum type damper 15, the rotation speed of the rotating body 16 is changed by the vibration of the transmitted damper passing torque T1. The rolling element 18 reciprocates along the rolling surface 19 in a state of being pressed against the rolling surface 19 by the centrifugal force. Such a deviation between the torsional vibration of the rotating body 16 and the pendulum motion of the rolling element 18 reduces the damper passing torque T1. That is, in the tenth embodiment, the reverse input torque Ti is reduced in two stages by the torsional damper 12 and the pendulum type damper 15, and the torque reduced in the two stages is transmitted to the speed reduction mechanism 4. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the tenth embodiment, the same operation and effect as each of the embodiments described above can be obtained. Can. In addition, since the pendulum type damper 15 is provided, the rolling elements 18 reciprocate according to the periodic reverse input torque input when traveling at a high vehicle speed, as in the eighth and ninth embodiments. By adjusting the pendulum length in the pendulum type damper 15 so as to move, it is possible to reduce the vibration due to the periodic reverse input torque Ti when traveling at a high vehicle speed.

Eleventh Embodiment
FIG. 13 is a skeleton diagram showing a vehicle drive system according to an eleventh embodiment of the present invention. In the example shown in FIG. 13, the torsional damper 12 is disposed on the output side of the motor 2 in the torque transmission direction from the motor 2 to the wheels 3, and the output shaft of the motor 2 or an input (not shown) of the reduction mechanism 4 The input side rotation member 12A of the torsional damper 12 is connected to the shaft. An output side rotation member 12B is connected to the input side rotation member 12A via a coil spring 12C. An inertial mass body 14 having a predetermined mass is integrally provided on the output side rotation member 12B. Since the other configuration is the same as that shown in FIG. 2, the same parts as those shown in FIG. 2 will be assigned the same reference numerals as in FIG. 2 and the description thereof will be omitted.

  The operation of the eleventh embodiment will be described. When the motor 2 outputs a torque, the torque is transmitted to the input side rotation member 12A of the torsional damper 12, and is transmitted to the output side rotation member 12B through the coil spring 12C. A torque for rotating the output side rotation member 12B and the inertial mass body 14 acts on the coil spring 12C as a reaction force. A load for compressing the coil spring 12C is generated by the so-called reaction force torque for rotating the output side rotation member 12B and the inertia mass body 14 and the output torque of the motor 2 transmitted to the input side rotation member 12A. Displacement occurs in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. That is, it twists. When there is no or stable torque fluctuation in the power transmission path, the entire torsional damper 12 integrally rotates in a state where the above-described torsion occurs. Further, the output torque of the motor 2 is increased according to the gear ratio of the reduction mechanism 4 and transmitted to the wheel 3.

  When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and is integrated with the input side rotation member 12A, the output side rotation member 12B and the output side rotation member 12B. Relative rotation with the inertial mass 14 occurs repeatedly. That is, it vibrates. Since the output side rotation member 12B and the inertia mass body 14 integral with the output side rotation member 12B are connected to the input side rotation member 12A via the coil spring 12C, the output side rotation member 12B and the inertia mass integrated therewith The phase of the vibration of the body 14 and the phase of the vibration of the input side rotation member 12A are out of phase. In the eleventh embodiment, such a deviation between the vibration of the input side rotation member 12A and the vibration of the output side rotation member 12B and the vibration of the inertial mass 14 integral with the output side rotation member 12B causes the reverse input torque Ti. Vibration of the power transmission path is reduced. Therefore, the reverse input torque Ti transmitted to the motor 2 and the fluctuation of the torque resulting therefrom are reduced or mitigated, so that even in the eleventh embodiment, the same operation and effect as each embodiment described above can be obtained. Can.

  The present invention is not limited to the embodiments described above, and the vehicle drive device 1 according to the embodiment of the present invention may be mounted on the vehicle body 11. FIG. 14 schematically shows a part of a so-called on-board type vehicle in which a vehicle drive device according to an embodiment of the present invention is mounted on a vehicle body. In the configuration shown in FIG. 14, since the vehicle drive device 1 is mounted on the vehicle body 11, the so-called unsprung load can be reduced, and the riding comfort of the vehicle and the contact of the tire 6 with the road surface can be improved. . In addition, even with such a configuration, since the fluctuation of the reverse input torque Ti transmitted to the motor 2 by the damper mechanism 5 and the torque resulting therefrom is reduced or mitigated, the same operation as each embodiment described above You can get the effect.

  DESCRIPTION OF SYMBOLS 1 ... Drive device for vehicles, 2 ... Motor, 3 ... Wheel, 5 ... Damper mechanism, 12 ... Torsional damper (damper mechanism), 13 ... Planetary gear mechanism (damper mechanism), 9 ... Pendulum type damper (damper mechanism), PT ... power transmission path.

To achieve the above object, the invention provides a vehicle drive device that generates driving force for traveling by transmitting a motor torque which caused the motor to the wheel, the motor, for each of the wheels provided in a power transmission path between the motor and the wheel, and a damper Organization you reduce variations in our Keru torque to the driveline, the rotational speed of the wheel relative to the rotational speed of said motor a speed reduction mechanism configured to a low speed vignetting set, the damper mechanism includes a first member disposed on the output side of the motor in the direction of transmission of the motor torque, direction of transmission of the motor torque The spring type damper having a second member disposed on the output side of the first member, an elastic body connecting the first member and the second member so as to allow relative rotation, and a plurality of rotating elements Planetary rotating machine for operation And the spring-type damper is provided on the output side of the reduction mechanism in the direction of transmission of the motor torque, and the first member is connected to a first rotation element of the plurality of rotation elements, The second member is connected to the second rotating element of the rotating elements, and the first rotating element and the second rotating element are relatively rotated by the fluctuation of the torque in the power transmission path. The third rotating element of the rotating elements of is rotated to generate an inertial torque .

FIG. 1 is a view schematically showing a part of a so-called in-wheel motor vehicle configured using a vehicle drive device according to an embodiment of the present invention. It is a skeleton figure showing the drive for vehicles concerning the 1st reference example of this invention. It is a skeleton diagram showing a vehicle driving apparatus according to a first implementation embodiment of the present invention. It is a skeleton diagram showing a vehicle drive device according to a second implementation embodiment of the present invention. It is a skeleton diagram showing a vehicle drive device according to a third implementation mode of the present invention. It is a skeleton diagram showing a vehicle drive device according to a fourth implementation mode of the present invention. It is a skeleton view of a vehicle drive device according to a fifth implementation mode of the present invention. It is a skeleton diagram showing a vehicle driving apparatus according to a sixth implementation mode of the present invention. It is a skeleton figure showing the drive for vehicles concerning the 2nd reference example of this invention. It is a figure which shows typically the pendulum type | mold damper shown in FIG. It is a skeleton figure showing the drive for vehicles concerning the 3rd reference example of this invention. It is a skeleton figure showing the drive for vehicles concerning a 4th reference example of this invention. It is a skeleton figure showing the drive for vehicles concerning a 5th reference example of this invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows typically a part of what is called on-board type vehicle which mounted the vehicle drive device which concerns on embodiment of this invention in the vehicle body.

Vehicle drive device according to an embodiment of the invention this is a device for generating a driving force for traveling of the vehicle, the vehicular drive system is provided for each wheel of the vehicle. FIG. 1 is a view schematically showing a part of a so-called in-wheel motor vehicle that is configured using a vehicle drive device according to an embodiment of the present invention. The vehicle drive device 1 shown in FIG. 1 includes a motor 2 as a driving force source, and is configured to transmit the motor torque generated by the motor 2 to the wheels 3. That is, the driving force generated by each wheel 3 can be controlled independently. The torque transmission path PT for transmitting the motor torque generated by the motor 2 to the wheels 3 corresponds to the power transmission path in the embodiment of the present invention. Moreover, the motor torque mentioned above is only described as torque in the following description.

FIG. 2 is a skeleton diagram showing a vehicle drive system according to a first embodiment of the present invention. As shown in FIG. 2, the stator 2S of the motor 2 is fixed to the case 8, and the rotor 2R is connected to the reduction gear mechanism 4 so as to be able to transmit torque. The motor 2 may be configured to perform energy regeneration at the time of deceleration, and as a motor performing energy regeneration at the time of deceleration, for example, a motor having a power generation function such as a permanent magnet synchronous motor can be mentioned. In FIG. 2, the suspension mechanism 9 and the lower arm 10 are omitted to simplify the drawing.

Next, the operation of the vehicle drive device 1 configured as shown in FIG. 2 will be described. When the motor 2 is subjected to powering control and outputs torque, the output torque of the motor 2 is increased according to the gear ratio in the reduction mechanism 4 and transmitted to the input-side rotating member 12A of the torsional damper 12 via the coil spring 12C. The torque is transmitted to the output side rotation member 12B of the torsional damper 12. Since the wheel 3 is connected to the output side rotation member 12B, torque for rotating the output side rotation member 12B and the wheel 3 acts on the coil spring 12C as a reaction force. The torque acting as a reaction force on the coil spring 12C is simply referred to as a reaction torque in the following description. A load for compressing the coil spring 12C is generated by the output torque of the motor 2 and the reaction torque transmitted to the input side rotation member 12A, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. That is, it twists. There is no variation in the torque transmitted by the power transmission route PT between the output torque and the reaction torque i.e. the motor 2 and the wheel 3 of the motor 2, or if the stable is twisted occurred previously described In the state, the entire torsional damper 12 integrally rotates.

Therefore, in the configuration described above, the expansion and contraction of the coil spring 12C in the torsional damper 12 causes the torque T1 in which the reverse input torque Ti is reduced to appear in the input side rotation member 12A. That is, it is possible to reduce or alleviate the fluctuation of the torque caused by the reverse input torque Ti or the reverse input torque Ti input from the wheel 3 to the motor 2. Therefore, control of the motor can be performed with high accuracy, and efficiency can be improved, and so-called electricity cost can be improved. Moreover, anti it is possible to reduce or mitigate the variation in the torque definitive in the power transmission route PT, for example, that the vibration caused by the meshing state of the gears with each other changes and with it the rattle in the deceleration mechanism 4 is caused Or it can be suppressed. Furthermore, since the motor 2 is not performing powering control, that is, in a so-called free state, resonance between the vibration of the motor 2 and the vibration of the reverse input torque Ti in the case where the natural frequency is decreasing is suppressed. Can. That is, the deterioration of the NVH characteristics can be avoided or suppressed. As a result, so-called robustness can be improved as a whole of the vehicle drive device 1.

(First implementation form)
Figure 3 is a skeleton diagram showing a vehicle driving apparatus according to a first implementation embodiment of the present invention. The example shown in FIG. 3 is an example in which the damper mechanism in the embodiment of the present invention is configured by the torsional damper 12 and the planetary gear mechanism 13. The planetary gear mechanism 13 is of a single pinion type, and holds a sun gear 13S, a ring gear 13R which is an internal gear disposed concentrically with the sun gear 13S, and a pinion gear 13P engaged with the sun gear 13S and the ring gear 13R. And a carrier 13C. The input side rotation member 12A of the torsional damper 12 is connected to the carrier 13C, and the output side rotation member 12B of the torsion damper 12 is connected to the sun gear 13S. An inertial mass body 14 having a predetermined mass is integrally provided on the ring gear 13R. Since the other configuration is the same as that shown in FIG. 2, the same parts as those shown in FIG. 2 will be assigned the same reference numerals as in FIG. 2 and the description thereof will be omitted.

The operation of the vehicle drive system 1 configured as shown in FIG. 3 will be described. When the motor 2 outputs a torque, the output torque is increased according to the gear ratio in the reduction mechanism 4 and is transmitted to the input side rotation member 12A of the torsional damper 12. A load for compressing the coil spring 12C is generated by the output torque of the motor 2 transmitted to the input side rotation member 12A and the above-described reaction torque, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. Since the sun gear 13S of the planetary gear mechanism 13 is connected to the output side rotation member 12B and the carrier 13C is connected to the input side rotation member 12A, the relative rotation between the input side rotation member 12A and the output side rotation member 12B The sun gear 13S and the carrier 13C rotate relative to each other by a predetermined angle. If or when torque is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3 is stable, the overall torsional damper 12 in a state resulting twisting described above integrally And rotate. Similarly, since the sun gear 13S and the carrier 13C integrally rotate in a twisted state, the entire planetary gear mechanism 13 integrally rotates.

Since the relative rotation between the input side rotation member 12A and the output side rotation member 12B is repeatedly generated by the vibration of the reverse input torque Ti, the relative rotation between the sun gear 13S and the carrier 13C is repeatedly generated according to the vibration of the reverse input torque Ti. Along with this, the pinion gear 13P of the planetary gear mechanism 13 rotates within a predetermined angle range, and the ring gear 13R is forcibly rotated. The ring gear 13R vibrates according to the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the ring gear 13R, the mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Further, in the example shown here, the rotational speed of the ring gear 13R is accelerated with respect to the rotational speed of the carrier 13C according to the gear ratio. Therefore, the rotational angular acceleration of the ring gear 13R and the inertial mass body 14 is increased, and the inertial torque T2 is increased accordingly. The inertia torque T2 acts on the input side rotation member 12A. Further, the phase of the vibration of the above-mentioned inertia torque T2 and the phase of the vibration of the damper passing torque T1 transmitted to the input side rotation member 12A through the torsional damper 12 are deviated. Therefore, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is reduced by the inertia torque T2 and becomes smooth. Thus, in the first implementation, the input side for the damper passing torque T1 appearing on rotating member 12A can be reduced by the inertia torque T2, the torque fluctuations due to the reverse input torque Ti and it is transmitted to the motor 2 can be reduced or alleviated first reference example by remote effectively. As a result, the control of the motor 2 can be performed with high accuracy, and the efficiency can be improved, and so-called electricity costs can be improved. Furthermore, it is possible to avoid or suppress the occurrence of gear rattling noise and vibration due to changes in the meshing state of the gears meshing with each other in the reduction gear mechanism 4 and the planetary gear mechanism 13. Thus even the first implementation embodiment can achieve the same operation and effect as the first embodiment.

(The second implementation form)
Figure 4 is a skeleton diagram showing a vehicle drive device according to a second implementation embodiment of the present invention. Damper mechanism in the third embodiment is an apparatus for changing a part of the configuration of the planetary gear mechanism in the damper mechanism shown in FIG. 3, in the second implementation embodiment, the output side rotational member of the torsional damper 12 to the carrier 13C 12B is connected, the input side rotation member 12A is connected to the ring gear 13R, and the inertia mass body 14 is provided on the sun gear 13S. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

A description of the operation of the second implementation embodiment. And even when the motor 2 is outputting torque, there is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable is above As described above, the entire torsional damper 12 integrally rotates. In addition, the entire planetary gear mechanism 13 rotates integrally.

When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the carrier 13C in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P in the planetary gear mechanism 13 rotates within a predetermined angle range, and the sun gear 13S is forcibly rotated. The sun gear 13S vibrates according to the vibration of the reverse input torque Ti. Since the inertia mass body 14 is integrally provided on the sun gear 13S, the mass (inertial moment) obtained by adding the mass of the sun gear 13S and the mass of the inertia mass body 14 and the inertia torque T2 according to the rotational angular acceleration are It occurs. Further, in the example shown here, the rotational speed of the sun gear 13S is accelerated with respect to the rotational speed of the ring gear 13R according to the gear ratio. Therefore, the rotational angular acceleration of the sun gear 13S and the inertial mass body 14 is increased, and the inertial torque T2 is increased accordingly. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even in the second implementation embodiment, similarly to the first actual施形state and the first reference example The effects and effects of

(Third implementation form)
Figure 5 is a skeleton diagram showing a vehicle drive device according to a third implementation mode of the present invention. Damper mechanism in a third implementation form, an apparatus for changing a part of the configuration of the planetary gear mechanism in the damper mechanism shown in FIG. 3, in the third implementation mode, the inertial mass 14 is provided on the carrier 13C, The ring gear 13R is connected to the input side rotation member 12A of the torsional damper 12, and the sun gear 13S is connected to the output side rotation member 12B. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

A description of the operation of the third implementation form. And even when the motor 2 is outputting torque, there is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable is above As described above, the entire torsional damper 12 integrally rotates. In addition, the entire planetary gear mechanism 13 rotates integrally.

When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the sun gear 13S and the ring gear 13R in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the carrier 13C is forcibly rotated, and vibrates in accordance with the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the carrier 13C, the mass (inertial moment) obtained by adding the mass of the carrier 13C and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even third implementation form, as with the embodiment type state and the first reference example described above The effects and effects of

(Fourth implementation form)
Figure 6 is a skeleton diagram showing a vehicle drive device according to a fourth implementation mode of the present invention. Damper mechanism in a fourth implementation form, an apparatus for changing a part of the configuration of the planetary gear mechanism in the damper mechanism shown in FIG. In a fourth implementation mode, is connected the output rotary member 12B of the torsional damper 12 to the carrier 13C, the input-side rotary member 12A is connected to the sun gear 13S, the inertial mass 14 is provided on the ring gear 13R. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

A description of the operation of the fourth implementation form. And even when the motor 2 is outputting torque, there is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable is above As described above, the entire torsional damper 12 integrally rotates. In addition, the entire planetary gear mechanism 13 rotates integrally.

When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the carrier 13C and the sun gear 13S in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the ring gear 13R is forcibly rotated, and the ring gear 13R vibrates according to the vibration of the reverse input torque Ti. Since the inertial mass body 14 is integrally provided on the ring gear 13R, the mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and the inertial torque T2 according to the rotational angular acceleration are It occurs. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is reduced and smoothed. become. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even fourth implementation form, the same action as each of type state and the first reference example・ We can get an effect.

(Fifth implementation form)
Figure 7 is a skeleton diagram showing a vehicle drive device according to a fifth implementation mode of the present invention. Damper mechanism in a fifth implementation form, an apparatus for changing a part of the configuration of the planetary gear mechanism in the damper mechanism shown in FIG. 3, in the fifth implementation mode, the inertial mass 14 is provided on the carrier 13C, The input-side rotation member 12A of the torsional damper 12 is connected to the sun gear 13S, and the output-side rotation member 12B is connected to the ring gear 13R. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 will be assigned the same reference numerals as in FIG. 3 and the description thereof will be omitted.

A description of the operation of the fifth implementation form. And even when the motor 2 is outputting torque, there is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable is above As described above, the entire torsional damper 12 integrally rotates. In addition, the entire planetary gear mechanism 13 rotates integrally.

When the reverse input torque Ti is input to the wheel 3, the compression force acting on the coil spring 12C changes. The coil spring 12C expands and contracts in accordance with the vibration of the reverse input torque Ti, and relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the sun gear 13S in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P rotates within a predetermined angle range, the carrier 13C is forcibly rotated, and vibrates in accordance with the vibration of the reverse input torque Ti. Then, a mass (inertial moment) obtained by adding the mass of the ring gear 13R and the mass of the inertial mass body 14 and an inertial torque T2 according to the rotational angular acceleration are generated. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even fifth implementation mode, as with the embodiment type state and the first reference example described above The effects and effects of

(Sixth implementation form)
Figure 8 is a skeleton diagram showing a vehicle driving apparatus according to a sixth implementation mode of the present invention. Damper mechanism in a sixth implementation form is a device for changing a part of the configuration of the planetary gear mechanism in the damper mechanism shown in FIG. 3, in the sixth implementation, the input-side rotation of the torsional damper 12 to the carrier 13C The member 12A is connected, the output side rotation member 12B is connected to the ring gear 13R, and the inertia mass body 14 is provided on the sun gear 13S. Since the other configuration is the same as that shown in FIG. 3, the same parts as those shown in FIG. 3 are assigned the same reference numerals as in FIG. 3 and the description thereof is omitted.

A description of the operation of the sixth implementation form. And even when the motor 2 is outputting torque, there is no variation in the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable is above As described above, the entire torsional damper 12 integrally rotates. In addition, the entire planetary gear mechanism 13 rotates integrally.

When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. Along with that, the ring gear 13R and the carrier 13C in the planetary gear mechanism 13 rotate relative to each other. Further, the pinion gear 13P is rotated within a predetermined angle range, the sun gear 13S is forcibly rotated, and vibrates according to the vibration of the reverse input torque Ti. Then, a mass (inertial moment) obtained by adding the mass of the sun gear 13S and the mass of the inertial mass body 14 and an inertial torque T2 according to the rotational angular acceleration are generated. Since the phase of the vibration of the inertia torque T2 and the phase of the vibration of the damper passing torque T1 are shifted, the inertia torque T2 acts as a damping torque with respect to the damper passing torque T1, and the damper passing torque T1 is the inertia torque T2. Is reduced and smoothed. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even sixth implementation mode, as with the embodiment type state and the first reference example described above The effects and effects of

( Second reference example)
A second embodiment of the present invention is shown in FIG. The example shown in FIG. 9 is an example which comprised the damper mechanism in embodiment of this invention by the pendulum type damper mechanism. The pendulum type damper mechanism is referred to as a pendulum type damper 15 in the following description. The pendulum type damper 15 is provided on the output side of the motor 2 in the transmission direction of the torque generated by the motor 2 and on the input side of the reduction mechanism 4 in the example shown here.

The operation of the second reference example will be described. When the motor 2 outputs a torque and the rotating body 16 rotates, the rolling elements 18 also rotate accordingly. The rolling element 18 is moved to a position farthest from the center of the rotating body 16 in the rolling chamber 17 by centrifugal force. That is, the rolling element 18 moves to a position on the rolling surface 19 farthest from the center of the rotating body 16. There is no variation of the torque transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable, the rolling element 18, the rotation center of the rotating body 16 in the rolling surface 19 It is pressed by the centrifugal force to the farthest point from.

Is reverse input torque Ti input to the wheel 3, when the torque of the torque, i.e. the rotating body 16 definitive in the power transmission route PT between the motor 2 and the wheel 3 changes, the rotational speed of the rotating body 16 changes. Along with this, the rolling element 18 performs a pendulum motion inside the rolling chamber 17 by inertia force. That is, it reciprocates along the rolling surface 19 in a state where it is pressed against the rolling surface 19 by the centrifugal force. The deviation between the pendulum movement of the torsional vibration and the rolling elements 18 in such a rotating body 16, the torque fluctuation in the power transmission route PT caused by the reverse input torque Ti and it is reduced. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even in the second reference example, the same as the exemplary type state and the first reference example described above It is possible to obtain actions and effects.

( Third reference example)
FIG. 11 is a skeleton diagram showing a vehicle drive system according to a third embodiment of the present invention. The example shown in FIG. 11 is an example in which the pendulum type damper 15 is disposed between the motor 2 and the reduction mechanism 4 in the transmission direction of the torque generated by the motor 2 and the torsional damper 12 is disposed on the output side of the reduction mechanism 4 It is. Since the other configuration is the same as that shown in FIG. 9, the same parts as those shown in FIG. 9 will be assigned the same reference numerals as in FIG. 9 and the description thereof will be omitted.

The operation of the third reference example will be described. When the motor 2 outputs a torque and the rotating body 16 rotates, the rolling elements 18 also rotate accordingly. The rolling element 18 moves to the farthest point from the center of the rotating body 16 on the rolling surface 19 by centrifugal force. Further, a load that the coil spring 12C compresses is generated by the output torque of the motor 2 transmitted to the input side rotation member 12A and the above-described reaction torque, and a displacement corresponding to the load is generated in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. No torque variation definitive in the power transmission route PT between the motor 2 and the wheel 3, or stable when to have, the rolling element 18, the farthest point from the center of the rotating body 16 in the rolling surface 19 Keep pressed by centrifugal force. Further, in the torsional damper 12, the entire torsional damper 12 rotates integrally as a result of the above-described torsion.

When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. By such expansion and contraction of the coil spring 12C, the reverse input torque Ti is reduced and transmitted to the input side rotation member 12A. The damper passing torque T1 appearing on the input side rotation member 12A is transmitted to the pendulum type damper 15 via the speed reduction mechanism 4. When the rotational speed of the rotating body 16 is changed by the damper passing torque T1, the rolling element 18 performs a pendulum motion inside the rolling chamber 17 by an inertial force. That is, it reciprocates along the rolling surface 19 in a state where it is pressed against the rolling surface 19 by the centrifugal force. Such a deviation between the torsional vibration of the rotating body 16 and the pendulum motion of the rolling element 18 reduces the damper passing torque T1. That is, in the third reference example, the reverse input torque Ti is reduced to two stages by the torsional damper 12 and the pendulum damper 15. Therefore, even in the third reference example, since the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, the exemplary shaped state and the reference examples and the same actions and effects You can get Further, as in the second reference example , the pendulum length in the pendulum type damper 15 is adjusted so that the rolling elements 18 reciprocate according to the periodic reverse input torque input when traveling at a high vehicle speed. Thus, it is possible to reduce the vibration due to the periodic reverse input torque Ti when traveling at a high vehicle speed.

( 4th reference example)
FIG. 12 is a skeleton diagram showing a vehicle drive system according to a fourth embodiment of the present invention. The example shown in FIG. 12 is an example in which the arrangement of the pendulum type damper 15 shown in FIG. 11 is changed. That is, the pendulum type damper 15 is disposed on the output side of the reduction mechanism 4 in the direction of transmission of the torque generated by the motor 2, and the torsional damper 12 is disposed on the output side of the pendulum type damper 15. Since the other configuration is the same as that shown in FIG. 11, the same parts as those shown in FIG. 11 will be assigned the same reference numerals as in FIG.

The operation of the fourth reference example will be described. When the motor 2 outputs a torque, the torque is increased according to the gear ratio of the reduction mechanism 4 and is transmitted to the pendulum type damper 15. When the rotating body 16 is rotated by the transmitted torque, the rolling element 18 is also rotated accordingly. The rolling element 18 moves to the farthest point from the center of the rotating body 16 on the rolling surface 19 by centrifugal force. Further, the coil spring 12C is compressed by the output torque of the motor 2 transmitted to the input side rotation member 12A and the reaction torque described above, and the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. . No torque fluctuations transmitted by the power transmission route PT between the motor 2 and the wheel 3, or if the stable, the rolling element 18, the most from the center of the rotating body 16 in the rolling surface 19 Maintain a state of being pressed by centrifugal force at a distant place. Further, in the torsional damper 12, the entire torsional damper 12 rotates integrally as a result of the above-described torsion.

When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and the relative rotation between the input side rotation member 12A and the output side rotation member 12B repeatedly occurs. By such expansion and contraction of the coil spring 12C, the reverse input torque Ti is reduced and transmitted to the input side rotation member 12A. A damper passing torque T1 appears on the input side rotation member 12A, and the damper passing torque T1 is transmitted to the pendulum damper 15. In the pendulum type damper 15, the rotation speed of the rotating body 16 is changed by the vibration of the transmitted damper passing torque T1. The rolling element 18 reciprocates along the rolling surface 19 in a state of being pressed against the rolling surface 19 by the centrifugal force. Such a deviation between the torsional vibration of the rotating body 16 and the pendulum motion of the rolling element 18 reduces the damper passing torque T1. That is, in the fourth reference example, the reverse input torque Ti is reduced in two stages by the torsional damper 12 and the pendulum type damper 15, and the torque reduced in the two stages is transmitted to the speed reduction mechanism 4. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even fourth reference example, the same as the exemplary type status and the reference examples described above act・ We can get an effect. Further, since the pendulum type damper 15 is provided, the rolling elements 18 reciprocate according to the periodic reverse input torque input when traveling at a high vehicle speed as in the second and third reference examples. By adjusting the pendulum length in the pendulum type damper 15 so as to move, it is possible to reduce the vibration due to the periodic reverse input torque Ti when traveling at a high vehicle speed.

( Fifth reference example)
FIG. 13 is a skeleton diagram showing a vehicle drive system according to a fifth embodiment of the present invention. In the example shown in FIG. 13, the torsional damper 12 is disposed on the output side of the motor 2 in the torque transmission direction from the motor 2 to the wheels 3, and the output shaft of the motor 2 or an input (not shown) of the reduction mechanism 4 The input side rotation member 12A of the torsional damper 12 is connected to the shaft. An output side rotation member 12B is connected to the input side rotation member 12A via a coil spring 12C. An inertial mass body 14 having a predetermined mass is integrally provided on the output side rotation member 12B. Since the other configuration is the same as that shown in FIG. 2, the same parts as those shown in FIG. 2 are assigned the same reference numerals as in FIG. 2 and the description thereof is omitted.

The operation of the fifth reference example will be described. When the motor 2 outputs a torque, the torque is transmitted to the input side rotation member 12A of the torsional damper 12, and is transmitted to the output side rotation member 12B through the coil spring 12C. A torque for rotating the output side rotation member 12B and the inertial mass body 14 acts on the coil spring 12C as a reaction force. A load for compressing the coil spring 12C is generated by the so-called reaction force torque for rotating the output side rotation member 12B and the inertia mass body 14 and the output torque of the motor 2 transmitted to the input side rotation member 12A. Displacement occurs in the coil spring 12C. As a result, the input side rotation member 12A and the output side rotation member 12B rotate relative to each other by a predetermined angle. That is, it twists. There is no variation of the torque definitive in the power transmission route PT, or, if you are stable, the entire torsional damper 12 rotate integrally in a state of twisted described above has occurred. Further, the output torque of the motor 2 is increased according to the gear ratio of the reduction mechanism 4 and transmitted to the wheel 3.

When the reverse input torque Ti is input to the wheel 3, the coil spring 12C expands and contracts according to the vibration of the reverse input torque Ti, and is integrated with the input side rotation member 12A, the output side rotation member 12B and the output side rotation member 12B. Relative rotation with the inertial mass 14 occurs repeatedly. That is, it vibrates. Since the output side rotation member 12B and the inertia mass body 14 integral with the output side rotation member 12B are connected to the input side rotation member 12A via the coil spring 12C, the output side rotation member 12B and the inertia mass integrated therewith The phase of the vibration of the body 14 and the phase of the vibration of the input side rotation member 12A are out of phase. In the fifth reference example , the reverse input torque Ti is caused by the deviation between the vibration of the input side rotation member 12A and the vibration of the output side rotation member 12B and the inertia mass body 14 integral with the output side rotation member 12B. vibrations of the power transmission route PT to is reduced. Accordingly, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated, even fifth reference example, the same as the exemplary type status and the reference examples described above act・ We can get an effect.

The present invention is not limited to the embodiments described above, and the vehicle drive device 1 according to the embodiment of the present invention may be mounted on the vehicle body 11. FIG. 14 schematically shows a part of a so-called on-board type vehicle in which a vehicle drive device according to an embodiment of the present invention is mounted on a vehicle body. In the configuration shown in FIG. 14, since the vehicle drive device 1 is mounted on the vehicle body 11, the so-called unsprung load can be reduced, and the riding comfort of the vehicle and the contact of the tire 6 with the road surface can be improved. . Also in this configuration, the fluctuation of the torque due to the reverse input torque Ti and it is transmitted to the motor 2 is reduced or alleviated by the damper mechanism 5, each of type state and the reference examples described above it is possible to obtain the same advantages as the.

Claims (5)

In a vehicle drive device for transmitting a motor torque generated by a motor to wheels to generate a driving force for traveling,
The motor is provided for each of the wheels.
A vehicle drive device according to claim 1, further comprising: a damper mechanism for reducing torque fluctuation in a power transmission path between the motor and the wheel. In the vehicle drive device according to claim 1,
The power transmission path is provided with a speed reduction mechanism configured such that the number of revolutions of the wheel is lower than the number of revolutions of the motor.
The damper mechanism includes a first member disposed on the output side of the motor in the transmission direction of the motor torque generated by the motor, and a first member disposed in the transmission direction of the motor torque generated by the motor. A spring type damper having a second member disposed on the output side, and an elastic body connecting the first member and the second member so as to allow relative rotation;
The said spring type damper is provided in the output side of the said reduction mechanism in the transmission direction of the said motor torque generated with the said motor, The vehicle drive device characterized by the above-mentioned. In the vehicle drive device according to claim 1,
The power transmission path is provided with a speed reduction mechanism configured such that the number of revolutions of the wheel is lower than the number of revolutions of the motor.
The vehicle drive device according to claim 1, wherein the damper mechanism includes a pendulum type damper having an inertial mass body that reduces fluctuation of the torque by reciprocating due to fluctuation of the torque in the power transmission path. In the vehicle drive device according to claim 3,
The damper mechanism includes a first member disposed on the output side of the motor in the transmission direction of the motor torque generated by the motor, and a first member disposed in the transmission direction of the motor torque generated by the motor. A vehicle drive device characterized by further comprising a spring type damper having a second member arranged on the output side, and an elastic body connecting the first member and the second member so as to allow relative rotation. . In the vehicle drive device according to claim 2,
The damper mechanism further includes a planetary rotation mechanism that performs a differential operation by a plurality of rotation elements,
The first member is connected to a first rotating element of the plurality of rotating elements, and the second member is connected to a second rotating element of the plurality of rotating elements,
The first rotation element and the second rotation element are relatively rotated by the fluctuation of the torque in the power transmission path, and the third rotation element of the plurality of rotation elements is rotated to generate an inertial torque. And a driving device for a vehicle.

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